Compressor-operating means



Nov. 19, 1929.

E. F. PETERSON 1,736,507

COMPRESSOR OPERATING MEANS 3 Sheets-Shet o O N O 7 Filed July 6, 1926Nov. 19, 1929. E. F. PETERSON 1,736,507

COMPRESSOR OPERATING MEANS Filed July 6, 1926 I 3 Sheets-Sheet 2 F E I wY 7 gwuento'o Edwin-1 PETEPEEITL Nov. 19, 1929. E. F. PETERSON 3COMPRESSOR OPERATING MEANS Filed July 6, 1926 5 Sheets-Sheet 3 v F i lm.

Patented Nov. 19, 1929 EDWIN F. PETERSON, OF MENQMINEE, 'MICH IGAN'COM-PRESSOR-OPEE- KTING MEANS Application filed July 6, 1926. Serial No.120,796.

The present invention relates to compres sors, primarily intended foruse 'as an air compressor.

The primary object of the invention is to provide an improved type ofair compressor operating under a novel principle whereby a constant anduniform delivery of air under compression will be delivered by thecompressor. 1 I I Q A further object of the invention is to pro-- vide acompressor embodying a plurality of cylinder-s and co-operating pistonswhich act successively for compressing of the air, thus resulting in nolost motion during operation of the compressor.

A further object of the invention is to pro-- vide an improved type ofair compressor'embodying a plurality of pairs of axially alignedcylinders with one of the pairs of cylinders serving as a low pressurecylinder and its'companion cylinder serving as a high pressure cylinder,and the plurality of pairs of cylinders co-acting with one another forserving as ashockabsorbing medium for the companion pairs of cylinders.

A still further object of the invention is to provide an air compressorembodying a novel actuating means for the cylinders whereby thecompressor is devoid of any cranks or wrist :pinsl A still furtherobjectof the invention resides in the provision of improved means whereby theopposed pistons ot' the compressor are caused toreciprocate in astraight I path when a rectilinear motion is :i'nnaa'rted to thepistons.

A still further object of the invention is to providela multiplecylinder, multiple stage, constant, :no lost motion air compressor whichis of extremely simple and durabl construction, and which compressorwill operate with comparatively little vibration, and which will also bepractically noiseless in its operation.

Other objects and advantages of the invention will be apparent duringthecourse of the "following detailed description, taken in connectionwith the accompanying drawings forming a part of this specification andin which drawings:

Figure 1 is a side elevation of the improved compressor and showing oneo-f-the-side-cover plates removed. i

Figure 2 is a horizontal section taken substantiallyon line2 2 ofFigure 1. v

Figure 3 is a vertical transverse section on line 3-3 of Figure 2 andlooking in the direction of the arrows. 1

Figure 4 is a vertical transverse section taken substantially on line i-d oi Figure 2 in the directionot the arrows, and showing the manner inwhich the pistons are retained in a straight path during theirreciprocato'ry motions.

Figure 5 isa sectional view taken substantially on line 55 of Figure 4;and looking in the direction of the arrows.

Figure 6 is a detail view of the drive cam for imparting a:reciprocatory motion to the pistons.

Fi ure :7 is an end View of the discharge end of the compressor.

Figure 8 is an end view of the intake end oi the compressor.

Figure 9 is a detailed sectional view on line 99 of Figure 10,, andshowing the contruction of the cross heads connecting the opposedpiston-s.

Figure 10 is a sectional View on line 1 0 m of Figure 9., and showingthe manner in which the opposed pistons are connected with the crosshead.

Figure 11 isa view partly in elevation and part in section, and showinga slightly modig tied for-m 0t cross head.

Figure 12 shows a still further modified form of the cross head.

Figure 13 is .a fragmentary perspective view of one end of the minor orroller guides for the cross heads. Referring to the drawings in detail,and wherein similar reference characters de'si g nate correspondingparts throughout the several views, 15 designates a suitable base plateupon which the compressor is intended toFbe mounted.

Mounted transversely upon the upper face or" the base plate 15, is apair of supporting plates 16 and 15 which are preferably square inoutline, and which preferably have right angular flanges 17 formed alongtheir lower edges and through which suitable bolts 18 may pass foranchoring of the plates in spaced parallel confronting relation. Each ofthe plates 16 and 16 is provided with symmetrically arranged aligningcircular shaped openings 19 which are arranged concentric to the axis ofthe plates.

Mounted in surface contact with the inner face of each of the supportingplates 16 and 16', are square bearing plates 20 and 20 re spectively,and which plates as will be observed in Figures 3 and 4, are arranged inangular relation to the supporting plates with their marginal edgesintersecting the supporting plate openings 19. These bearing plates 20are preferably secured to their respective supporting plates by means ofheaded bolts 21 which pass inwardly thru the supporting plates withtheir shanks threaded into the corner portions of the bearing plates.The intermediate portion of each marginal edge of each of the bearingplates 20 and 20, is provided with semi-circular shaped depressions 22which align with the openings 19 of the respective supporting plates towhich the bearing plates are attached. These semi-circular shapeddepressions 22 serve as a further anchoring means for the supportingplates, in a manner to be subsequently explained.

Revolubly mounted axially of the supporting plates as by a suitablebearing 23 and an end thrust bearing 24 carried by the plates 16 and 16respectively, is a drive shaft 25 which may be driven from any suitablesource of power. The bearings 23 and 24 are preferably of the rollertype as illustrated in Figure 3, meta suitable stuffing box 26 ispreferably provided for the drive shaft 25 where it extends thru thebearing 23. The end thrust bearing 24 is preferably in the form of a capbolted to the outer face of the supporting plate 16.

A drive cam 28 is mounted upon the drive shaft 25 between the bearingplates 20 and 20, and is secured to the drive shaft for rotationtherewith as by means of suitable keys 29. Provided in the peripheralface of the cylindrical shaped drive cam 28, is an endless cam groove 30having its opposite terminals disposed at diametrically opposite sidesof the drive cam. Thrust bearing washers 31 are provided at each end ofthe drive cam 28, and which washers are intended for hearing relationagainst the confronting faces of the bearing plates 20 and 20 forpreventing longitudinal shifting'of the drive cam when being rotated bythe drive shaft 25. This cylindrical shaped drive cam 28 is preferablyof a diameter such that when the cam is mounted between the bearingplates, the circumferential face of the cam will be spaced but a slightdistance inwardly from the axial center of the aligning openings 19,Thisconstruction is clearly illustrated in Figure 4 of the drawings.

Carried by the supporting plate 16, and extending longitudinally of thebase plate 15, is a group of four low pressure cylinders 32 havingannular flanges 33 provided adjacenttheir inner ends for abutting withthe outer face of the supporting plate when the cylinders are inassembled relation to the plates. Extending inwardly from the annu larflanges 33 of each cylinder, are tubular skirt portions 34 of a diameterto snugly fit within the openings 19 with the inner ends of the skirtportion disposed flush with the inner face of the bearing plate 20.Suitable bolts 35 extend through the flanges 33 and are threaded intothe supportingplate 16 for rigid mounting of the low pressure cylindersin parallel relation upon the supporting plate. open ends of the lowpressure cylinders 32, and all of which are of similar construction,open inwardly of the supporting plate 16. Closing the outer end of eachof the cylinders 32, are cylinder heads 36 provided with horizontallyaligned ports 37 Directly connected with the outer port of each of thecylinder heads 36, is an automatically operable valve 38, and each ofwhich connect with transfer ducts 39 which extend longitudinally of thecompressor to each side of the supporting plates 16 and 16. Connectingeach upper and lower set of the low pressure cylinders 32, andcommunicating with the inner ports 37 of the cylinder heads, is a doubleacting check valve 40 provided with a screened intake 41. This doubleacting check valve 40, as will be observed in Figure 2, acts forautomatically checking egress of air from the low pressure cylindersduring their compression strokes. By observing Figure 8, it will be seenthat by so connecting the upper and lower sets of low pressure cylinders32 by means of the double acting check valve 40, permits of a suitablespace being provided between the cylinders through which the drive shaft25 may extend for connection to a suitable source of power for impartinga rotary movement to the shaft.

Arranged in axial alignment with each of the low pressure cylinders 32,and carried by the supporting plate 16, are high pres sure cylinders 42of an internal diameter and area less than that of their opposed lowpressure cylinders. These high pressure cylinders 42 are also providedwith annular flanges 43 adapted tobear against the outer face of thesupporting plate 16, and skirt portions 44 which extend through thesupporting plate openings 19 with their ends flush with the inner faceof the bearing plate 20'. Bolts 45 extend through the flanges 43 forrigidly mounting of the cylinders in parallel relation upon thesupporting plate 16. Closing the outer end of each of the high Thus itwill be seen that the inner,

pressure cylinders 42, is a cylinder head '46 providedat its outer sidewith a horizontally opening port 47 and provided at its end face withanexhaust portion 47 An automatically operable check valve 48 is connectedat the outer side of each of the heads 46, at the ports 47, andrespectively connect with the discharge end of the respective transferducts 39. Thus it will be seen that each of the high pressure cylinders42 are connected withtheir companion low pressure cylinders 32 by meansof an independent transfer duct 39. Connected with each of theterminally opening,- exhaust ports 47 of each of the cylinder heads 46,is a check valve 49, and all of which open into a collector 50 whichconnects all of the high pressure cylinders 42 with a common outlet pipe51 leading to a pressure tank or for use in any preferred manner. Byobserving Figure 7, it will be seen that the collector 50 embodies apair of vertically disposed pipes 52 connecting the top-and bottomcylinders, and which pipes 52 are connected at their intermediateportions by a horizontally disposed pipe section 53-which leads to thecommon outlet pipe 51.

Reciprocally mounted in each of the aligning companion pairs ofcylinders32 and 42, areopposed pistons 55 and 56, adapted for movement in thecylinders 32 and 42 respectively. As will readily be observedin Figure5, the piston 55 is of greater diameter than that of'the piston 56, andthat thepistons are provided with a desired number of piston rings forcausing the pistons to fit snugly within their respective cylinders.Connected with eachof the pistons 55 and 56, and extending in axialalignment toward one another, are piston or connecting rods 57 connectedat their inner ends by means of a crosshead 58. Thiscross head 58embodies a substantially rectangularly shaped connecting block 59 havingthreaded openings 60 provided in axial alignment at each end thereof forthreaded reception of the threaded innerends of the piston rods 57. Locknuts 61 threaded upon the inner end of the piston rods 57, are adaptedto be turned into binding engagement with the end faces of theconnecting blocks for preventing possible disconnection of the rods fromthe connect ing block. Fitted about the outer andside faces of theconnecting block 59, is a substantially U-shaped guide bearing 62 havingits side arms 63 provided with longitudinally extending guide grooves64. Extending transversely through the connecting block 59 and guidebearing 62, is a carrier pin 65 having a bearing portion 66 provided atthe inncrsideof the connecting block for rotatable mounting. of atubular shaped cam roller 67. This bearing portion 66.pr0vides ashoulder atthe inner end-ofthe carrier pin for engagingthe inner face ofthe connecting block, and that portionofthe carrier pin directlyoutwardly ofthe outer face of the guide hearing 62, is: threaded as at68 for receiving suitable jam nuts 69 which, when turned into bindingengagement with the guide bearing, secure the carrier pin againstrotation wit in thecross head, and also rigidly connect the guidebearing 62 with the connecting block 59, Provided on the carrier pin 65outwardly of the threaded portion 68, is a second or outer bearingportion 7 O for rotatablev mounting of atubular shaped guide roller 71.The outer terminal end of the carrier pin may-be threaded for receivingsuitable lock nuts 7 2 for securing the roller 71 against movement oilthe carrier pin.

Extending longitudinally of the base plate 15, and between thesupporting plates 16 and 16, are main or cross head guides 75 havingtheir opposite ends rigidly secured to the edges of the respectivebearing plates 20 and 20 as by suitable fastening elements such as capscrews76. These guides 75, and two of which are disposed at each edge ofthe bearing plates, serve as guides for the cross heads 58 for causingthe pistons 55 and 56 to move in straight paths within their respectivecylinders. As will be observed in Figure 4, the inner edges of thecompanion guides 75 receive the longitudinally extending guide grooves64 provided in the side arms of the guide bearings 62. By observingFigure 3, it will be seen that the transversecenters of the main guides75 intersect the axis of the aligned cylinders 32 and 42. It may here bewell to state that these guides 75 by reason of being anchored at theirends to the bearing plates 20 and 20,serve as a tie for rigidlyretaining the supporting plates 16 and 16 in proper parallel spacedapart relation.

When the cross heads 58 are mounted be tween the guides 7 5, theirrespective cam rollers 67 will be disposed in the cam groove 30 of thedrive cam 28, with their carrier pins 65 extending in directionsradially of the drive cam and toward each corner of the squaresupporting plates 16 and 16.

Rig-idly mounted at the inner face of each of the supporting plates 16and 16, and at each corner portion of the plates, are L-shaped brackets78 having oil'set portions 79 extend ing in parallel relation with theside edges of the'bearing plates 20 and 20. These brackets 78 areeachadapted to support longitudinally extending spaced roller guides 80which are preferably secured to the inner faces of the ofiiset portions79 as by suitable bolts 81. These roller guides 80 are provided withfiat confronting faces 82 between which the guide roller 71 moves duringreciprocation of the cross head 58. By observing Figure 4, it will beseen that these guide rollers 71 and coacting guides 80 serve to preventbinding of the cross heads 58 upon the guides 75 and thus permit of freeand easy movement ofthe cross heads along their guides.

' spectively, are or ried by the side and top edges of the supportingplates 16 and 16 for enclosing the structures between the supportingplates, and providing a housing for receiving a lubricant in liquid formfor lubricating of the moving parts operating between the supportingplates. A suitable filler opening 87 may be provided in the top coverplate for the placing of the lubricant within the housing formed by thecover plates, and a 1 suitable drain opening 88 may be provided in thebase plate for draining of the lubricant when desirable. This inclosingof the movable portions between the supporting plates will not onlyprovide an effective 1 method of lubrication, but will also tend tocause the compressor to operate with but comparatively little noise.

By so providing the arcuate shaped recesses in the edges of the bearingplates 20 and 21, and allowing the skirt portions of the cylinders toextend into the recesses, will permit of the bearing plates being morerigidly held against possible rotary movement and which movement wouldcause the main guides 75 to move out of proper aligning relation withthe cylinders.

\Vith reference to the form of cross-head as shown in Figure 11, thebearing portion 66 disposed at the inner side of the connecting block59, as well as the threaded portion 68 and the bearing portion disposedat the outer side of the connecting block, are shown as forming anintegral structure, with the cam roller 67 held in position by a capscrew In the form of cross head as illustrated in Figure 12, the guideroller 71 has been dispensed with, and when using this type of crosshead the roller guides 80 are not necessary.

By referring to Figure 2, and wherein the pistons are shown in positionin the lowermost pairs of cylinders. and when the drive cam is moving inthe direction of the arrow, the connected pistons will be moving in a direction of the arrows as illustrated at the respective cylinders. Thecompanion pairs of cylinders have been marked A, B, C, and D. Uponmovement of the piston within the cylinder B and in a direction of thearrow, air will be drawn through the screened intake e1 opening thecheck va ve leading to the head 36 of the low pressure cylinder B and atwhich time the check valve 38 ofthe low pressure cylinder B is closed.At the same time, the piston of the high pressure cylinder B is movingtoward. the cylinder head 46 and compressing its charge through theexhaust port 47 and into the collector 50. The check valve 48 is closedduring the compression stroke of the high pressure piston 56, thusentrapping compressed air from the low pressure cylinder B in thetransfer duct 39. Upon return movement of the connected pistons 55 and56, the intake check valve will automatically close and allow thecompressed air in the low pressure cylinder to be forced through thetransfer duct 39, opening both of the check valves 38 and 48, and enterthe high pressure cylinder during the suction or intake stroke of thehigh pressure piston. During the last mentioned operation, the checkvalved?) automatically closes. Each of the cylinders A, B, C and D,operates in a like manner and in successive order, thus causing aconstant and uniform delivery of air under pressure to the common outletpipe 51.

The pitch of the endless cam groove 80 may be varied for providing adesired stroke of the connected pistons 55 and 56.

From the foregoing description it will be apparent that a compressorembodying novel features construction has been provided whereby theconnected pistons are retained in a true straight path of movementwithin their respective cylinders, and which pistons successivelyoperate for providing an efficient multiple stage compressor having nolostmo tion, and producing a uniform and constant delivery of air to acommon outlet pipe. It will also be apparent that a novel arrangement ofparts has been incorporated in the compressor whereby the movableportions of the compressor act in an eiiicient manner in an extremelycompact form.

Various changes may be made to the speciiic form and arrangement ofparts herein shown and described, without departing from the spirit ofthe invention or the scope of the following claims.

I claim:

1. In motion transmitting mechanism for converting continuous rotarymotion into rectilinear reciprocatingmotion, the combination with a pairof spaced apart supporting plates, of a drive shaft revolubly mounted inthe plates and provided with a cam groove disposed between the plates,companion sets of elements reciprocally movable in a path parallel withthe axis of rotation of the drive shaft, rods connecting companion setsof reciprocatory elements and extending parallel with the drive shaft,cross heads rigidly carried by said rods between the plates and havingguide and cam rollers mounted upon their outer and inner facesrespectively, guides connected between the supporting plates andproviding tracks for the cross heads, said cam roller of the cross headsto engage in the cam groove of the drive shaft and be held againstdisplacement by said cross head guides, and

further guides carried by the supporting plates outwardly of said crosshead guides for receiving the guide roller mounted at the outer face ofsaid cross heads.

2. In motion transmitting mechanism for converting continuous rotarymotion into rectilinear reciprocating motion, the combination with apair of spaced apart supporting plates, of a drive shaft revolublymounted in the plate and provided with a cam groove disposed between theplates, a rod reciprocally movable in a path parallel with the axis ofrotation of the drive shaft, a cross head rigidly carried by the rodbetween the plates, guides for the cross head, a carrier pin for thecross head extending in a direction radially of the drive shaft andprojecting from the inner and outer faces of the cross head, a rollermounted on the carrier pin at the inner side of the cross head forengaging in the cam groove of the drive shaft, a roller mounted upon thecarrier pin at the outer side of the cross head, and guides for saidlast mentioned roller.

3. In motion transmitting mechanism for converting continuous rotarymotion into rectilinear reciprocating motion, the combination with apair of parallel spaced apart square supporting plates, of a drive shaftrevolubly mounted in the plates and provided with a cam groove disposedbetween the plates, companion sets of reciprocally movable elementsmovable in a path parallel with the axis of rotation of said driveshaft, rods connecting each companion set of reciprocally movableelements and extending longitudinally of the drive shaft between theplates, means carried by each rod and engageable in said cam groove forimparting reciprocatory motion to the rods, bearing plates rigidly carried by the inner face of each supporting plate in angular relation tothe supporting plates, main guides carried by and connected at theirends to the edges ofthe bearing plates, and roller guides carried by thesupporting plates outwardly of said main guides, said main and rollerguides to co-act with said cam engaging means for guiding the companionsets of reciprocally movable elements and their respective connectingrods in a straight path of movement.

EDWIN F. PETERSON.

